CA1098460A - Self-aligning clutch release bearing - Google Patents
Self-aligning clutch release bearingInfo
- Publication number
- CA1098460A CA1098460A CA324,117A CA324117A CA1098460A CA 1098460 A CA1098460 A CA 1098460A CA 324117 A CA324117 A CA 324117A CA 1098460 A CA1098460 A CA 1098460A
- Authority
- CA
- Canada
- Prior art keywords
- bearing
- carrier
- spring washer
- assembly
- bearing carrier
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/43—Clutches, e.g. disengaging bearing
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Support Of The Bearing (AREA)
Abstract
SELF-ALIGNING CLUTCH
RELEASE BEARING
Abstract of the Disclosure A self-aligning clutch release bearing assembly in-cluding a tubular bearing carrier and a anti-friction bearing assembly encircling the bearing carrier and supported thereon by means of an annular spring washer which enables relative restricted shifting movement of the axis of the bearing relative to the axis of the bearing carrier to compensate for eccentricity in the axis of rotation of a clutch assembly and a guide member on which the clutch release bearing assembly is mounted. In addition, the spring washer permits restricted angular dis-placement of the axis of the bearing assembly relative to the axis of the bearing carrier to compensate for angular mis-alignment between the clutch assembly and axis of reciprocation of the clutch release bearing assembly. The bearing carrier further includes coacting means for engaging a clutch actuating device such as a actuating fork for preventing relative rotation of the clutch release bearing assembly whereby an adjustment for radial misalignment by the bearing assembly is appropriately maintained during subsequent clutch actuation cycles.
RELEASE BEARING
Abstract of the Disclosure A self-aligning clutch release bearing assembly in-cluding a tubular bearing carrier and a anti-friction bearing assembly encircling the bearing carrier and supported thereon by means of an annular spring washer which enables relative restricted shifting movement of the axis of the bearing relative to the axis of the bearing carrier to compensate for eccentricity in the axis of rotation of a clutch assembly and a guide member on which the clutch release bearing assembly is mounted. In addition, the spring washer permits restricted angular dis-placement of the axis of the bearing assembly relative to the axis of the bearing carrier to compensate for angular mis-alignment between the clutch assembly and axis of reciprocation of the clutch release bearing assembly. The bearing carrier further includes coacting means for engaging a clutch actuating device such as a actuating fork for preventing relative rotation of the clutch release bearing assembly whereby an adjustment for radial misalignment by the bearing assembly is appropriately maintained during subsequent clutch actuation cycles.
Description
~0'~89L6~ 1 ~ackground oÇ the Invention . , Various types of clutch release or throw-out bearing assemblies have heretofore been used or proposed for use in the drive train of automobiles and the like equipped with manual transmissions. The relatively severe operating conditions to which clutch release bearing assemblies are subjected during service has prompted continuing development of improved designs for providing positive and quiet oper~tion over an increased operating life. The relative severity of the operating con-ditions to which clutch throw-out bearings are subjected are in at least part attributable to the intermittent loading to which they are subjected, the relatively abrupt imposition of loading and rotational forces during the actuation and release of a clutch assembly, the marginal lubricating conditions to which they are subjected during operation, the effect of vibration on the wear of the operating components as well as a misalignment of the axis of the clutch release bearing and the .
axis of rotation of the rotating clutch assembly imposing a non-uniform distribution of loading on the assembly.
The continuing development work has resulted in substantial improvements in the operating efficiency, durability and life of clutch release assemblies some of which further in-clude devices for providing sel-f-adjustment for misalignment between the axis of the release assembly and the axis of rotation of the clutch and release members thereon. In some of the prior art designs, the self-adjusting alignment action occurs each time the clutch mechanism is actuated with the release bearing assembly returning to a neutral position after the clutch is reengaged. This repeated self-adjusting action
axis of rotation of the rotating clutch assembly imposing a non-uniform distribution of loading on the assembly.
The continuing development work has resulted in substantial improvements in the operating efficiency, durability and life of clutch release assemblies some of which further in-clude devices for providing sel-f-adjustment for misalignment between the axis of the release assembly and the axis of rotation of the clutch and release members thereon. In some of the prior art designs, the self-adjusting alignment action occurs each time the clutch mechanism is actuated with the release bearing assembly returning to a neutral position after the clutch is reengaged. This repeated self-adjusting action
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an~ the relative movement between the eompollellts to eo~ ens~tc for a misaligned condition h~s resulted in inere~sed wear and a eorresponding reduction in the useful operating life of the release bearing assembly. In other prior art eonstructions, at least a portion of the self-adjusting aetion is retained oveir-coming certain of the deficiencies of other prior art self-aligning eluteh release assemblies. Unfortunately, eluteh release assemblies ineorporating self-aligning features in aeeordallce with prior art practicos are relatively eomplex rendering them somewllat eostly to manufaeture and assemble.
Typical of such prior art constructions are t1lose as disclosed in United States Patents 3,416,637; 3,815,715; 3,~77,557;
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an~ the relative movement between the eompollellts to eo~ ens~tc for a misaligned condition h~s resulted in inere~sed wear and a eorresponding reduction in the useful operating life of the release bearing assembly. In other prior art eonstructions, at least a portion of the self-adjusting aetion is retained oveir-coming certain of the deficiencies of other prior art self-aligning eluteh release assemblies. Unfortunately, eluteh release assemblies ineorporating self-aligning features in aeeordallce with prior art practicos are relatively eomplex rendering them somewllat eostly to manufaeture and assemble.
Typical of such prior art constructions are t1lose as disclosed in United States Patents 3,416,637; 3,815,715; 3,~77,557;
3,900,091; and 4,029,186.
It is, aceordingly, a prineipal objeet of the present invention to provide for an improved self-aligning elutch release bearing assembly which overcomesmany of the problems and disadvantages associated with prior art eonstruetions and which is of simple design, durable operation, which possesses self-aligning capability, and which is of eeonomieal manufaeture.
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Summary of the Invention ,` The benefits and advantages of the present invention are aehieved by a self-aligning eluteh release bearing assembly of a type adapted to be reciprocally mounted on a guide member such as a transmission support tube disposed substantially eo-axial with the axis of rotation of a eluteh and eluteh aetuating means of the type employed in automotive power trains or the like. The clutch release assembly is reeiprocable along the ~` guide member by suitable actuating means such as an aetuating :
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fork conncctcd to thc clutch pcdal of a vchiclc cquippcd with a manually shiftahlc transmission. Thc clutch rcle~sc bearing assembly includcs a tubular bearing carricr slidably mountcd on the guidc mcmber and a bc~ring suppDrtcd on the bearing carrier including a plurality of anti-friction elements interposed between a stationary race member and a rotatable race me~ber.
The rotatable race member is provided with an engaging face adaptcd to cngage the clutcll relcase mcans during a clutch operating c)~cle.
The stationary race member, in accordance with one embodiment of the present invention, is formed with a bore defining an internal surface disposed in spaced relationship around the periphery of the bearing carrier and includes an inwardly extending groove in which the peripheral portion of a spring washer is disposed permitting restricted relative shifting movement between the axis of the bearing carrier and the bearing in response to an eccentric misalignment condition between the axis of the guide member and the rotational axis of the clutch. Additionally, the spring washer is resiliently displaceable in an axial direction to enable restricted angular displacement of the axis of the bearing relative to the axis of the bearing carrier to compensate for an angular misalignment condition between the axis of the guide member and the rotational axis of the clutch. The inner portion of the spring washor is suitably restrained against relative longitudinal movemcnt on the bearing carrier such as by means of an inwardly extending groove around the periphery of the bearing carrier.
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Thc bcaring carricr is furthcr providcd, in accordancc with a prcfcrrcd cmbo~imcnt of thc prcscnt invcntion, with ~
radially projccting flangc at its rearw~rd end which is formcd with a radially extcnding notch for engaging thc clutch actuating means or fork whcreby relative rotation of the clutch release assembly after the first clutch opcrating cycle is prevented whereby the radial adjustment of the bearing to correct an cccentric misalignn1cnt condition is rctai11cd dllring subsequent clutch opcrating cycles. Thc hearing carrier preferably is formed of a rolled tubular sheet and the flange is integrally formed at one end such as by upsetting. The internal surface of the bearing carrier preferably is provided with one or more recesses adapted to receive and retain a reservoir of a lubricant to facilitate reciprocating movement of the clutch release assembly along the guide member.
In accordance with an alternative embodiment of the present invention, the inner race member rotates and the outer race member is stationary. According to one form of this embodiment, the periphery of the external surface of the outer stationary race member is formed with an inwardly extending groove in which the inner portion of the spring washer is disposed permitting restricted relative shifting movements of th~ bearing assembly with respect to the bearing carrier to compensate for a misalignment condition. The bearing carrier is provided with an annular housing encircling the periphcry of the stationary race member and disposed in spaced clearance relationship thereto for receiving and engageably supporting the periphery of thc spring washer.
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In summary, then, the present invention is broadly defined as a clutch release bearing assembly including a tubular bearing carrier, a bearing supported on the bearing carrier including a stationary race member, a rotatable race member, and a plurality of anti-friction elements interposed between the race members, the stationary race member formed with an internal surface disposed in radial spaced clearance relation-ship relative to the periphery of the bearing carrier, an annular groove extending inwardly of the internal surface, a spring washer disposed with its outer edge portion in axially biased preloaded engagement within the groove and its inner edge portion in supporting relationship with the bearing carrier to permit restricted radial shifting movement between the carrier and the bearing and restricted angular displacement of the bearing relative to the axis of the carrier, the spring washer com-prising plural layers of a helically would serpentine strip of spring steel.
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~ dditional benefits and a~vantages of thc prcscnt invention will beeome npparent upon a reading of thc dcscription of the preferred embodiments taken in conjunetion with the aceompanying drawings.
Brief Deseription of the Drawings Figure 1 is a longitudinal vertieal seetional view of a sel~ liglling cllltch release beuring assembly constructed in aecordanee with one of the embodiments of the present in- ;
vention and showins an actuating fork fragmentarily;
'Figure 2 is a longitudinal vertieal seetional view of a clutch release bearing assembly constructed in accordance with an alternative embodiment of the present invention;
Figure 3 is a perspective view with a portion thereof broken away of a bearing carrier component of the clutch release assembly illustrated in Figures 1 and 2;
Figure 4 is a perspective view of a spring washer -employed in the clutch release bearing assemblies of Figures 1 and 2;
Figure 5 is a seetional view through a clutch release bearing assembly constructed in aeeordanee with an alternative embodiment of the present invention and taken along the line 5-5 of Figure 6;
Figure 6 is an end elevational view of the cluteh release bearing assembly shown in Figure 5; and Figures 7 through 10 are front elevational views of spring washers formed to provide for an inereased interlocking engagement with the bearing carrier.
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Descri~tion of the Preferrcd Eml)odiments -Referring now in detail to the drawings and as may be best seen in Figure 1, a clutch release bearing assembly con-structed in accordance with one of the embodiments of the present invention is shown and comprises a tubular bearing carrier 6 adapted to be slidably mounted on a guide member 8 as shown in phantom which may typically comprise a tubular support affixed to and projectillg forl~ardly of a transmission (not shown) througl which the transmission sllaft extends. The guide member is disposed with its axis 10 substantially coaxial with the axis of rotation of a rotatable clutch ~not shown) including clutch release means such as release fingers 12 as shown in phanton in Figure 1. The self-aligning characteristics of the clutch release bearing assembly subsequently to be described are intended to compensate for unavoidable misalignment conditions resulting from manufacturing tolerances and assembly techniques wherein the axis 10 is parallel to but eccentric or offset from the axis of rotation of the rotary clutch and release fingers 12 providing for an eccentric misalignment condition as well as where the axis 10 is angularly inclined relative to the axis of rotation of the rotary clutch and release fingers 12 causing an angular misalignment condition.
Referring again to Figure 1, an anti-friction bearing assembly 14 is supported in encircling radially spaced relationship around the tubular bearing carrier 6 and includes a rotatable race member 16 which is formed at its forward end or left hand end as viewed in Figure 1 with n radially inwardly extending flange 18, the annular exterior face 20 of which defines an engaging face for coacting with the ends of the .
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clutch release fingers 12 during actuation of thc clutchmechanism. The bearing assembly 14 further includes a plurality of anti-friction elements such as balls 22 intcrposcd betwccn thc rotatable race member 16 and an inner stationary race member 24. Preferably the bearing assembly 14 is of the angular contact type to withstand the thrust loads imposed thereon.
The stationary race member 24 is provided with an axi:~l re~rw~lrd extension 26 termin;lting in a subst;lntially radial annular face 2S whicll is adapted to be disposed in bearing contact with the end of clutch actuating means such as an actuating fork 30 as fragmentarily shown in Figure 1. The bearing assembly 14 is supported or suspended in radially spaced substantially concentric relationship with respect to the periphery of the bearing carrier 6 by means of a spring washer 32 as best seen in Figure 4 which is seated along its inner edge portion in a groove 34 extending around the periphery of the bearing carrier preventing relative axial movement between the bearing carrier and spring washer. The groove 34 is of a width slightly greater than the thickness of the spring washer to facilitate assembly. The inner diameter of the spring washer in a free, unstressed condition as shown in Figure 4 is slightly smaller than the diameter of the base of the groove 34 whereby the spring washer is in a circumferentially biased condition when seated in the groove 34 \~ith the inner edges thereof in gripping engagement around the bearing carrier restricting relative movement therebetween.
The outer peripheral portion of the spring washer 32 is disposed in axially biased interlocking relationship within an annular groove 36 extending radially inwardly of the surface ,- , :: .
of a circul;lr ~orc 38 through thc stationary racc mcmbcr 24.
The nnntllar groove 36 is dcfincd by a pair of axi~lly spacod substantiall~ parallcl and radially cxtcndin~ sidcwalls 40 terminating at an cnd wall 42 defining the depth of the groove.
As will be notcd in Figure 1, the outcr diametcr of the spring washer 32 is slightly smaller than thc diameter of the end wall 42 of the annular groove 36 providinc for radial clearance thcrcbctwccn for thc purposcs subse~uelltly to bc dcscribed.
Refcrring now in dctail to ~;gure 4, thc spring washcr 32 in accordance with a preferred embodiment of the present invention comprises a spirally or helically wound strip of substantially constant diameter of a resilient material such as spring steel to form a plurality of overlying layers. As sho~m, the helically wound strip is of a generally flat rectangular cross-sectional configuration and is deformed so as to incorporate a serpentine configuration comprising a repetitive series of axially projecting crests 44 and troughs 46. When the spring washer comprises a plurality of overlying layers in accordance with the arrangement illustrated in Figure 4, the circumferential disposition of the crests and troughs are offset from one layer to the next layer to provide for axial resilient compaction to a resilient preloaded condition when disposed in interlocked relationship within the annular groove 36 of the stationary race member (Figure 1). The spring washer 32 of Figure 4 is further characterized as being resiliently deformable from its unloaded condition as shown in Figure 4 to reduce its external diameter and to increase its internal diameter in response to relative sliding movement of the serpcntine layers over each othcr as rcquircd during installation and asscmbly of thc rcleasc bearings.
In accordancc with thc spccific arrangcmcnt illus-tratcd in ~iglJTC 1, thc spring washcr 32 is first inst;llled in thc annular groovc 36 of thc st:-tionary racc mcmbcr by radially deflccting the spring washcr inwar~ly to rcduce its cxternal diameter to cnable insertion thereof into the bore through the stationary race mcmber. Thc spring washer thercafter is moved along the interior bore until it radially expands and snaps into the annul~r groove 36. The width of thc annulnr groove is lcss tll;ln tllC axi;ll t~idtil of thc spring wilsllcr so as to providc some axial preloading of the spring washcr during initial assembly.
Thereafter the spring washer is radially expanded provided by the clearance between its periphery and the end wall 42 of the groove enabling the unflanged end of the tubular bearing carrier to be inserted therethrough and advanced until the spring washer snaps into interlocking relationship in the peripheral grcove 34 around the bearing carrier. By an appropriate disposition of the crests and troughs in the serpentine strip defining the spring washer, a relative camming coaction therebetween is effected during the assembly operation including a further pre-loading of the spring washer in an axial direction causing the axial faces thereof to bear under high pressure against the opposed surfaces of the side wall 40 defining the groove. Such preloading and the axial bearing coaction between the spring washer and the side walls of the annular groove 36 serve to suspcnd the bearing assembly 14 around the bearing carrier 6 in a manner to permit restricted relative radial movement there-between to compensate for eccentric misalignment conditions and to furthcr pcrmit angular deflection or skcwing of the bearillg asscmbly relativc to the axis of the bearing carrier -10- , .
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to compcnsatc for angular misalignmcnt conditions. In this conncction, it will bc apprcciatcd from thc structural fcaturcs of thc sprin~ washcr 32 as shown in ~igurc 4, that a limitcd axial rcflection of thc spring washcr is providcd in planes angularly tilted with respect to a plane pcrpcndicular to the axis of the bearing carrier thcreby providing for adjustment of an angular misalignment condition between the bearing cnrrier a~is and the axis of rotation o~ tlle clutch mechanism.
In accord;~nce with the forcgoing rcsilicnt suspcnsion system restricted radial movement of thc bearing assembly 14 relative to the bearing carrier 6 is permitted from a neutral or concentric position as shown in solid lines in Figure 1 to a radially and angularly adjusted position as shown in phantom providing for an automatic adjustment of eccentric and angular misalignment conditions. The axial biasing force applied by the spring washer 32 retains the bearing assembly and carrier in the radially offset position between operating cycles of the clutch such that the adjusted aligned condition is maintained so long as it prevails. The radial shifting force to effect the automatic adjustment is provided by the forces applied to the rotatable race member 16 as a result of the coaction of the clutch release fingers 12 against the engaging face 20 thereof. The resilicncy of the spring washer provides for quick adjustment of any angular misalignment condition prevalent at the initiation of each clutch actuation cycle and the bearing assembly is returned to a neutral position in which its axis of rotation is parallel to that of the benring carrier after the clutch is reengaged and the relcase fingcrs are disengaged.
The radial displ~cement of thc bcaring asscmbly 14 relative to thc bcaring carricr is limitcd by thc conction bctwccn thc periphcry of thc spring was11cr 32 and thc end wall 42 of thc annular groove.
Rcferring now in detail to Figure 3 of thc drawings, a tubular bearing carrier 6 is shown which is constructed in accordance with a prcferred embodimcnt of the present invention.
In the specific arrall~ement illustratcd, the bearing carrier i~s formcd as a wral)pcd-luslling cnal-ling ecollomical mallufacturc rom a flat sllcet of metal utilizing a scries of punch-prcss operations in accordance with the techniques well known in the art. The sheet material preferably comprises steel although it is also contemplated that any formable sheet material can be employed for this purpose. It is also contemplated that the sheet material may be of a composite construction including a lining of a bearing material along its inner surface such as by employing a clad bi-metal sheet.
In accordance with normal forming techniques, sheet steel is first blanked to an appropriate si~e during which the groove 34 is applied to one surface of the sheet. In addition, it is also contemplated that appropriate grooves or cavities such as the groove 4~ can be applied to the opposite surface of the sheet serving as reservoirs for retaining and distributing a lubricating material such as grease in the form of a film betwecn the inncr surface of the bearing carrier and the pcriphcry of the guidc member on which it is reciprocably and slidably mounted. During the blanking operation, the opposed edges 50, 52 are formcd with one or a plurality of longitudinally spaced tear-shapcd tabs 54 and corresponding tcar-shapcd apcrturcs 56, rcspcctivcly, which arc rollcd into intcrlocking relatiollship . ~ :
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lQ~ 6~:) during the subsequent rolling operation forming thereby ~ so-ealled clinch-butt joint. While the blanked and rolled eon-struction as shown in Figure 3 comprises a preferred embodiment, it will be understood that the tubular bearing carrier can also be fabricated from an integral tubular stock as well as by machining from solid bar stock.
After the rolling operation, the tubular benrin~
carriel is subjected to a final COill;ng operation to ef~ect a firm interlocking and clinching of the tabs and apertures ~s well as an upsetting operation to form a radially projecting flange 58 at one end of the bearing carrier. ~uring the up-setting operation, a V-shaped radially outwardly diverging notch or slot 60 is formed in the flange the sides of which are defined by the divergenee of the opposed edges 50 and 52 of the original blanked sheet. The V-shaped notch provides the important function of serving as a detent or coacting means for interlocking with the clutch actuating means or fork to prevent relative rotation of the bearing carrier and the stationary race member suspended thereon relative to the guide member.
Referring again to Figure 1, it will be noted that the actuating fork 30 includes a rearwardly extending cantilever spring member 62 which normally is provided in accordance with prior art constructions to provide a preloading of the actuating fork against the actuat;ng face 28 of the bearing assembly preventing rattling and noise as a result of vibration. In the present instance, the provision of the V-shaped notch interlocks with the depending portion of the cantilever spring 62 thereby preventing relative rotation of the bearing carrier and the guide member. During assembly of the clutch release :' ' ' bearing assembly, it is not necessary to angularly position thc V-shaped notch to eEfect an interlocking with the cantilever spring since during the first clutch actuation, the torque applied to the bearing assembly will cause rotation of the bearing carrier until the V-shaped notch is aligned with the spring 62 whereafter the clutch release bearing assembly will be retained in fixed position on the guide member. It will be furtller noted in the arIangement ;Is illustrated in ~i~ure 1 that the axial thrust of the actuating fork 30 is trallsmitted directly to the bearing assembly 14 and not through the bearing carrier 6.
~ eferring now to Figure 2 of the drawings, an alternative embodiment of the clutch release bearing assembly is illustrated in which like parts are designated by the same numeral as employed in Figure 1 with a prime affixed thereto.
As shown, the assembly includes a tubular bearing carrier 6' on which a bearing assembly 14' is suspended and which includes a rotatable race member 16' for~ed with an outwardly projecting radial flange 18' defining an engaging face 20' adapted to eoact with the elutch release means of a rotary elutch assembly.
A plurality of anti-friction elements such as balls 22' are interposed between the rotatabie race member and a stationary race member 24' which is formed at its rearward end or ri~ht hand end as viewed in ~i$ure 2, with a radial annular face 28' disposed against a stabili~ation eollar or washer 64. An actuating fork 30' is disposed in bearing contact against the opposite face of the stabilization eollar 64 and includes a cantilaver spring 62' adayted to be disposed in interlocking relationship within the V-shaped groove formed in the radial flan~e 5~' of the bearing earrier.
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As in the e~se of tl-e eml)odiment illustrated in Pigure 1, the arr~n~ement Or ligure 2 includes a spring washer 32' interlocked around the bearin~ carrier 6' by means of a groove 34' and is disposed with its peripheral portion in pre-loaded axial biased contact against the axial surfaces of an annular groove 36' which extends inwardly of a eireular bore 38' through the stationary race member 24'. The arrangement illustrltod in iig~lre 2 ;s similar to th3t previolJs~y deseribed in eonneetion with ~igure 1 and provides for similar self-alignment adjustment with respect to eccentrie misali~nment co~ditions and angular misalignment conditions of the axis of the guide member relative to the axis of rotation of the rotary clutch and release means thereon. The principal distinction resides in the relative disposition of the rotary and stationary raee members providing for a heavy duty cluteh release bearing assembly providing for increased life under heavy loads at high rotational speeds. The provision of the stabilization collar 64 is optional and is preferably eomprised of a blank steel washer whieh is disposed in the form of a press fit around the periphery of the bearing earrier 6'. The stabilization eollar 64 provides for added baeking support to the stationary race member 24' and further supports the clineh-butt joint of the bearing carrier in aceordance with the arrangement illustrated in Figure 3.
Referring now to Pigures S and 6 of the drawings, still another ~lternative embodiment of a elutch release bearing assembly is illustrated in which the outer race member is stationary while the inner race member is rotatable and wherein tho stationary race member is supported by a wave spring engaged J i ~
. ' ~ . ' ' in the periphery thereof in contrast to the embodiment illus-trated in Figure 2 in which the wave spring is engaged in a groove in the inner surface of the stationary race member. As shown in ~igures 5 and 6, the clutch release bearing assembly comprises a composite bearing carrier consisting of a tubular member 66, an oval-shaped flange 68 affixed to the rearward or right hand portion of the tubular member as viewed in Figure 5 alld all a~ ]ly projectillg ;~nntllar hollsing 70 encircling a bearing assembly 72. The inner surfilce of the tubular member 66 is formed with a groove 74 and a plurality of indentations 76 fo~ retaining a lubricant such as grease, facilitating reciproeat-ing movement of the lubular member along a guide tube (not shown) such as the tube 8 illustrated in phantom in Figure 1. The oval-shaped flange 68 is seeurely mounted on the tubular member 66 by means of a press fit within a groove on the right hand end of the tubular member as viewed in Figure 5. The tubular member is provided with a radial annular flange 77 to further seeure the assembly together. The ends of the flange 68 are bent to form a pair of rearwardly,extending tabs or ears 78 provided with apertures 80 for securing the bearing carrier to an aetuating fork (not shown).
The annular housing 70 extends in spaeed substantially eoncentric relationship with respect to the periphery of the tubular member 66 and is seeured to the flange 68 by means of bent tabs 82 disposed in interloeking engagement in recesses 84 formed along the edge of the flange as best seen in Figure 6.
The flange 68 is conveniently produeed by a stamping operation and is formed to provide two arcuate recesses 86 which project axially forwardly of the plane of the flange and are adapted to , .:
abut the inner edge of a station.lry race mcml>er 88 of the bearing Dssembly 72 maintaining it in al)propriate axinlly spaced relationship. The periphery or outer surf:~ce of the stationary race mem~er is disposed in radial clearance re-lationship with respect to the inner surface of the annular housing to provide for restricted radial shifting movement of the benring assembly relative to the composite bearing carrier.
For this purpose, the exterior surface of the stationary race member SS is formed with an inwardly extending annular groove 90 in which the inner edge portion of a wave spring 92 is seatably engaged in a manner similar to that previously described in connection with Figures 1 and 2. The inner edge of the wave spring 92 is disposed in clearance relationship with respect to the base of the annular groove 90 to permit restricted radial shifting movement of the bearing assembly relative to the composite bearing carrier to provide for correction of an eccentric misalignment condition. Similarly, the wave spring is def~ectable to also permit angular tilting of the bearing assembly to correct for an angular misalignment condition in a manner as previously described.
The outer edge of the wave spring 92 is disposed in engaging and supported relationship against the inner annulaT
surface of the housing 70. The outer or left hand end of the housing 70 as viewed in Figure S is formed with an inwardly directed flange 9~ to prevent inadvertent extraction of the bearing assembly from the housing.
The bearing assembly 72 may be of any of the types previously described and includes a rotatable inner race member 96 of a length projecting axially beyond the end of the .~ , .:
6!:) tubular mcmbcr 66 forming an nnnul.lr contact face 98 which is adaptcd to cngarc the clutch rclease fingcrs in a manncr as previously dcscribcd. Thc intcrnal surfacc o~ the inner race membcr 96 is spaccd in radial clcarance rclationship with respect IO the periphery of the tubular member to permit radial shifting movements as well as angular tilting movements of the bearing assembly to correct for misalignment conditions.
As shown in Figurc 5 a plllr~lity of anti-friction elcmellts or balls 100 arc interposed bctwcell the stationary and rotatable spaced relationship by means of a cage 102. An elastic annular seal 104 is secured along the forward inner edge of the stationary race member 88 and extends radially inwardly in sealing engagement with the peripilery of the rotatable race member. The seal 104 serves to retain a suitable lubricant such as grease ~ithin the bearing assembly. An annular disc 106 overlies the inner or right hand end of the bearing races as viewed in Figure S to restrict entry of con-taminating substances into the bearing assembly.
It will be apparent from the arrangement of the bearing assembly illustrated in Figures 5 and 6 that radial and angular shifting movements of the bearing assembly are permitted in a manner as previously described in connection with Figures 1 and 2. The axial thrust load from the actuating fork connected to the ears 78 of the composite bearing carrier is transmitted through the arcuate recesses 86 of the flange directly to the inner end of the stationary race member.
As prcviously described in connection with the embodi-ment shown in Figure 1 the inner diameter of the spring washcr 32 in a free unstressed condition is slightly smallcr than the ' ' ' `
diameter of the base of tlle groove 34 o~ t11e bearing earrierwhereby the spring washer i5 in a cireumferentially binsed eondition when seated in tl~e groove with the inner edges thcreof in gripping engagement around the be~ring carrier restricting relative movement therebetween. Similarly, in conneetion with the embodiment shown in Figures 5 and 6, the outer diameter of the spring washer in a free, unstressed condition is slightly larger t}lan tlle internal di~meter of the an?lular housing such that the syrinS w;lsiler is in a circulnferentially biased con-dition when positioned within the housing in accordance with the arrangement shown in Figure 5 such that the outer edges thereof are disposed in gripping engagement with the housing restricting relative rotative movement therebetween.
In order to further increase the gripping engagement between the spring washer 32 and the groove 34 of the bearing earrier 6, 6' in accordance with the arrangement shown in Figures 1 and 2, the ends of a wave spring 108 as shown in Figure 7 can be provided with inwardly directed barbs or burrs 110 which are adapted to bite or become embedded in the soft metal surface of the bearing carrier within the grooves 34, 34' thereby forming a mechanical interloek therebetween. The base of the groove 34, 34' can also be provided with surface roughness or irregularities in addition to the butt joint eonnection 45, as best seen in Figure 3 to further increase the frictional and mechanical gripping or interlock between the wave spring and the bearing carrier preventing relative circumferential movement therebetween. When the wave spring 108 of Figure 7 is employe~l in the arrangement illustrated in Figure 5, the barbs 110 project radially outwardly from the periphery of the spring _19_ .r so as to become embedded and mechallieally interloeked with the surface of tlle annular hol-sing 70. The form~tion of the baros 110 on the ends of the wave spring c~n be conveniently formed during the shearing of the wave spring strip into individual lengths prior to coilin~.
It is also eontemplated that in lieu of the barbs 110 of the embodiment illustrated in Figure 7, a wave spring 112 as shown in Figure S can be formed such that the terminnl portions thereof are of a reduced radius so th;lt the shnrp inwardly direeted eorners or edges 114 thereof ~end to beeome embedded and mechanically interlocked in the softer base metal of the grooves 34, 34' of the bearing carrier. Alternatively, a wave spring 116 is illustrated in Figure 9 in which the terminal portions of the spring are of an increased radius such that the sharp terminal edges 118 thereof project outwardly and are adapted to become embedded in the inner surface of the annular housing 70 of the embodiment illustrated in Figure 5.
Still another alternative embodiment of a wave spring 120 is illustrated in Figure 10 in which the inner and/or outer edges thereof are provided with staked V-shaped notches to provide a plurality of inwardly directed barbs 122 as well as outwardly directed barbs 124 disposed at circumferentially spaced intervals around the wave spring thereby further enhancing a mechanical gripping interaction with the base of the groove of the bearing carrier in accordance with the embodiments of Figure 1 and 2 or with the inner surface of the annular housing in accordance with the embodiment of Figure 5, respectively.
`. ', ~Q9t~46 While it will be ~pparent th.lt the invention herei disclosed is well calculated to acllieve tlle benefits and advant~ges as hcreinabove set forth, it will be ~ppreciate~
th~t the invention is susceptiblc to modification, variation and chan~e without departing from the spirit thereof.
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It is, aceordingly, a prineipal objeet of the present invention to provide for an improved self-aligning elutch release bearing assembly which overcomesmany of the problems and disadvantages associated with prior art eonstruetions and which is of simple design, durable operation, which possesses self-aligning capability, and which is of eeonomieal manufaeture.
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Summary of the Invention ,` The benefits and advantages of the present invention are aehieved by a self-aligning eluteh release bearing assembly of a type adapted to be reciprocally mounted on a guide member such as a transmission support tube disposed substantially eo-axial with the axis of rotation of a eluteh and eluteh aetuating means of the type employed in automotive power trains or the like. The clutch release assembly is reeiprocable along the ~` guide member by suitable actuating means such as an aetuating :
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fork conncctcd to thc clutch pcdal of a vchiclc cquippcd with a manually shiftahlc transmission. Thc clutch rcle~sc bearing assembly includcs a tubular bearing carricr slidably mountcd on the guidc mcmber and a bc~ring suppDrtcd on the bearing carrier including a plurality of anti-friction elements interposed between a stationary race member and a rotatable race me~ber.
The rotatable race member is provided with an engaging face adaptcd to cngage the clutcll relcase mcans during a clutch operating c)~cle.
The stationary race member, in accordance with one embodiment of the present invention, is formed with a bore defining an internal surface disposed in spaced relationship around the periphery of the bearing carrier and includes an inwardly extending groove in which the peripheral portion of a spring washer is disposed permitting restricted relative shifting movement between the axis of the bearing carrier and the bearing in response to an eccentric misalignment condition between the axis of the guide member and the rotational axis of the clutch. Additionally, the spring washer is resiliently displaceable in an axial direction to enable restricted angular displacement of the axis of the bearing relative to the axis of the bearing carrier to compensate for an angular misalignment condition between the axis of the guide member and the rotational axis of the clutch. The inner portion of the spring washor is suitably restrained against relative longitudinal movemcnt on the bearing carrier such as by means of an inwardly extending groove around the periphery of the bearing carrier.
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Thc bcaring carricr is furthcr providcd, in accordancc with a prcfcrrcd cmbo~imcnt of thc prcscnt invcntion, with ~
radially projccting flangc at its rearw~rd end which is formcd with a radially extcnding notch for engaging thc clutch actuating means or fork whcreby relative rotation of the clutch release assembly after the first clutch opcrating cycle is prevented whereby the radial adjustment of the bearing to correct an cccentric misalignn1cnt condition is rctai11cd dllring subsequent clutch opcrating cycles. Thc hearing carrier preferably is formed of a rolled tubular sheet and the flange is integrally formed at one end such as by upsetting. The internal surface of the bearing carrier preferably is provided with one or more recesses adapted to receive and retain a reservoir of a lubricant to facilitate reciprocating movement of the clutch release assembly along the guide member.
In accordance with an alternative embodiment of the present invention, the inner race member rotates and the outer race member is stationary. According to one form of this embodiment, the periphery of the external surface of the outer stationary race member is formed with an inwardly extending groove in which the inner portion of the spring washer is disposed permitting restricted relative shifting movements of th~ bearing assembly with respect to the bearing carrier to compensate for a misalignment condition. The bearing carrier is provided with an annular housing encircling the periphcry of the stationary race member and disposed in spaced clearance relationship thereto for receiving and engageably supporting the periphery of thc spring washer.
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In summary, then, the present invention is broadly defined as a clutch release bearing assembly including a tubular bearing carrier, a bearing supported on the bearing carrier including a stationary race member, a rotatable race member, and a plurality of anti-friction elements interposed between the race members, the stationary race member formed with an internal surface disposed in radial spaced clearance relation-ship relative to the periphery of the bearing carrier, an annular groove extending inwardly of the internal surface, a spring washer disposed with its outer edge portion in axially biased preloaded engagement within the groove and its inner edge portion in supporting relationship with the bearing carrier to permit restricted radial shifting movement between the carrier and the bearing and restricted angular displacement of the bearing relative to the axis of the carrier, the spring washer com-prising plural layers of a helically would serpentine strip of spring steel.
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~ dditional benefits and a~vantages of thc prcscnt invention will beeome npparent upon a reading of thc dcscription of the preferred embodiments taken in conjunetion with the aceompanying drawings.
Brief Deseription of the Drawings Figure 1 is a longitudinal vertieal seetional view of a sel~ liglling cllltch release beuring assembly constructed in aecordanee with one of the embodiments of the present in- ;
vention and showins an actuating fork fragmentarily;
'Figure 2 is a longitudinal vertieal seetional view of a clutch release bearing assembly constructed in accordance with an alternative embodiment of the present invention;
Figure 3 is a perspective view with a portion thereof broken away of a bearing carrier component of the clutch release assembly illustrated in Figures 1 and 2;
Figure 4 is a perspective view of a spring washer -employed in the clutch release bearing assemblies of Figures 1 and 2;
Figure 5 is a seetional view through a clutch release bearing assembly constructed in aeeordanee with an alternative embodiment of the present invention and taken along the line 5-5 of Figure 6;
Figure 6 is an end elevational view of the cluteh release bearing assembly shown in Figure 5; and Figures 7 through 10 are front elevational views of spring washers formed to provide for an inereased interlocking engagement with the bearing carrier.
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Descri~tion of the Preferrcd Eml)odiments -Referring now in detail to the drawings and as may be best seen in Figure 1, a clutch release bearing assembly con-structed in accordance with one of the embodiments of the present invention is shown and comprises a tubular bearing carrier 6 adapted to be slidably mounted on a guide member 8 as shown in phantom which may typically comprise a tubular support affixed to and projectillg forl~ardly of a transmission (not shown) througl which the transmission sllaft extends. The guide member is disposed with its axis 10 substantially coaxial with the axis of rotation of a rotatable clutch ~not shown) including clutch release means such as release fingers 12 as shown in phanton in Figure 1. The self-aligning characteristics of the clutch release bearing assembly subsequently to be described are intended to compensate for unavoidable misalignment conditions resulting from manufacturing tolerances and assembly techniques wherein the axis 10 is parallel to but eccentric or offset from the axis of rotation of the rotary clutch and release fingers 12 providing for an eccentric misalignment condition as well as where the axis 10 is angularly inclined relative to the axis of rotation of the rotary clutch and release fingers 12 causing an angular misalignment condition.
Referring again to Figure 1, an anti-friction bearing assembly 14 is supported in encircling radially spaced relationship around the tubular bearing carrier 6 and includes a rotatable race member 16 which is formed at its forward end or left hand end as viewed in Figure 1 with n radially inwardly extending flange 18, the annular exterior face 20 of which defines an engaging face for coacting with the ends of the .
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clutch release fingers 12 during actuation of thc clutchmechanism. The bearing assembly 14 further includes a plurality of anti-friction elements such as balls 22 intcrposcd betwccn thc rotatable race member 16 and an inner stationary race member 24. Preferably the bearing assembly 14 is of the angular contact type to withstand the thrust loads imposed thereon.
The stationary race member 24 is provided with an axi:~l re~rw~lrd extension 26 termin;lting in a subst;lntially radial annular face 2S whicll is adapted to be disposed in bearing contact with the end of clutch actuating means such as an actuating fork 30 as fragmentarily shown in Figure 1. The bearing assembly 14 is supported or suspended in radially spaced substantially concentric relationship with respect to the periphery of the bearing carrier 6 by means of a spring washer 32 as best seen in Figure 4 which is seated along its inner edge portion in a groove 34 extending around the periphery of the bearing carrier preventing relative axial movement between the bearing carrier and spring washer. The groove 34 is of a width slightly greater than the thickness of the spring washer to facilitate assembly. The inner diameter of the spring washer in a free, unstressed condition as shown in Figure 4 is slightly smaller than the diameter of the base of the groove 34 whereby the spring washer is in a circumferentially biased condition when seated in the groove 34 \~ith the inner edges thereof in gripping engagement around the bearing carrier restricting relative movement therebetween.
The outer peripheral portion of the spring washer 32 is disposed in axially biased interlocking relationship within an annular groove 36 extending radially inwardly of the surface ,- , :: .
of a circul;lr ~orc 38 through thc stationary racc mcmbcr 24.
The nnntllar groove 36 is dcfincd by a pair of axi~lly spacod substantiall~ parallcl and radially cxtcndin~ sidcwalls 40 terminating at an cnd wall 42 defining the depth of the groove.
As will be notcd in Figure 1, the outcr diametcr of the spring washer 32 is slightly smaller than thc diameter of the end wall 42 of the annular groove 36 providinc for radial clearance thcrcbctwccn for thc purposcs subse~uelltly to bc dcscribed.
Refcrring now in dctail to ~;gure 4, thc spring washcr 32 in accordance with a preferred embodiment of the present invention comprises a spirally or helically wound strip of substantially constant diameter of a resilient material such as spring steel to form a plurality of overlying layers. As sho~m, the helically wound strip is of a generally flat rectangular cross-sectional configuration and is deformed so as to incorporate a serpentine configuration comprising a repetitive series of axially projecting crests 44 and troughs 46. When the spring washer comprises a plurality of overlying layers in accordance with the arrangement illustrated in Figure 4, the circumferential disposition of the crests and troughs are offset from one layer to the next layer to provide for axial resilient compaction to a resilient preloaded condition when disposed in interlocked relationship within the annular groove 36 of the stationary race member (Figure 1). The spring washer 32 of Figure 4 is further characterized as being resiliently deformable from its unloaded condition as shown in Figure 4 to reduce its external diameter and to increase its internal diameter in response to relative sliding movement of the serpcntine layers over each othcr as rcquircd during installation and asscmbly of thc rcleasc bearings.
In accordancc with thc spccific arrangcmcnt illus-tratcd in ~iglJTC 1, thc spring washcr 32 is first inst;llled in thc annular groovc 36 of thc st:-tionary racc mcmbcr by radially deflccting the spring washcr inwar~ly to rcduce its cxternal diameter to cnable insertion thereof into the bore through the stationary race mcmber. Thc spring washer thercafter is moved along the interior bore until it radially expands and snaps into the annul~r groove 36. The width of thc annulnr groove is lcss tll;ln tllC axi;ll t~idtil of thc spring wilsllcr so as to providc some axial preloading of the spring washcr during initial assembly.
Thereafter the spring washer is radially expanded provided by the clearance between its periphery and the end wall 42 of the groove enabling the unflanged end of the tubular bearing carrier to be inserted therethrough and advanced until the spring washer snaps into interlocking relationship in the peripheral grcove 34 around the bearing carrier. By an appropriate disposition of the crests and troughs in the serpentine strip defining the spring washer, a relative camming coaction therebetween is effected during the assembly operation including a further pre-loading of the spring washer in an axial direction causing the axial faces thereof to bear under high pressure against the opposed surfaces of the side wall 40 defining the groove. Such preloading and the axial bearing coaction between the spring washer and the side walls of the annular groove 36 serve to suspcnd the bearing assembly 14 around the bearing carrier 6 in a manner to permit restricted relative radial movement there-between to compensate for eccentric misalignment conditions and to furthcr pcrmit angular deflection or skcwing of the bearillg asscmbly relativc to the axis of the bearing carrier -10- , .
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to compcnsatc for angular misalignmcnt conditions. In this conncction, it will bc apprcciatcd from thc structural fcaturcs of thc sprin~ washcr 32 as shown in ~igurc 4, that a limitcd axial rcflection of thc spring washcr is providcd in planes angularly tilted with respect to a plane pcrpcndicular to the axis of the bearing carrier thcreby providing for adjustment of an angular misalignment condition between the bearing cnrrier a~is and the axis of rotation o~ tlle clutch mechanism.
In accord;~nce with the forcgoing rcsilicnt suspcnsion system restricted radial movement of thc bearing assembly 14 relative to the bearing carrier 6 is permitted from a neutral or concentric position as shown in solid lines in Figure 1 to a radially and angularly adjusted position as shown in phantom providing for an automatic adjustment of eccentric and angular misalignment conditions. The axial biasing force applied by the spring washer 32 retains the bearing assembly and carrier in the radially offset position between operating cycles of the clutch such that the adjusted aligned condition is maintained so long as it prevails. The radial shifting force to effect the automatic adjustment is provided by the forces applied to the rotatable race member 16 as a result of the coaction of the clutch release fingers 12 against the engaging face 20 thereof. The resilicncy of the spring washer provides for quick adjustment of any angular misalignment condition prevalent at the initiation of each clutch actuation cycle and the bearing assembly is returned to a neutral position in which its axis of rotation is parallel to that of the benring carrier after the clutch is reengaged and the relcase fingcrs are disengaged.
The radial displ~cement of thc bcaring asscmbly 14 relative to thc bcaring carricr is limitcd by thc conction bctwccn thc periphcry of thc spring was11cr 32 and thc end wall 42 of thc annular groove.
Rcferring now in detail to Figure 3 of thc drawings, a tubular bearing carrier 6 is shown which is constructed in accordance with a prcferred embodimcnt of the present invention.
In the specific arrall~ement illustratcd, the bearing carrier i~s formcd as a wral)pcd-luslling cnal-ling ecollomical mallufacturc rom a flat sllcet of metal utilizing a scries of punch-prcss operations in accordance with the techniques well known in the art. The sheet material preferably comprises steel although it is also contemplated that any formable sheet material can be employed for this purpose. It is also contemplated that the sheet material may be of a composite construction including a lining of a bearing material along its inner surface such as by employing a clad bi-metal sheet.
In accordance with normal forming techniques, sheet steel is first blanked to an appropriate si~e during which the groove 34 is applied to one surface of the sheet. In addition, it is also contemplated that appropriate grooves or cavities such as the groove 4~ can be applied to the opposite surface of the sheet serving as reservoirs for retaining and distributing a lubricating material such as grease in the form of a film betwecn the inncr surface of the bearing carrier and the pcriphcry of the guidc member on which it is reciprocably and slidably mounted. During the blanking operation, the opposed edges 50, 52 are formcd with one or a plurality of longitudinally spaced tear-shapcd tabs 54 and corresponding tcar-shapcd apcrturcs 56, rcspcctivcly, which arc rollcd into intcrlocking relatiollship . ~ :
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lQ~ 6~:) during the subsequent rolling operation forming thereby ~ so-ealled clinch-butt joint. While the blanked and rolled eon-struction as shown in Figure 3 comprises a preferred embodiment, it will be understood that the tubular bearing carrier can also be fabricated from an integral tubular stock as well as by machining from solid bar stock.
After the rolling operation, the tubular benrin~
carriel is subjected to a final COill;ng operation to ef~ect a firm interlocking and clinching of the tabs and apertures ~s well as an upsetting operation to form a radially projecting flange 58 at one end of the bearing carrier. ~uring the up-setting operation, a V-shaped radially outwardly diverging notch or slot 60 is formed in the flange the sides of which are defined by the divergenee of the opposed edges 50 and 52 of the original blanked sheet. The V-shaped notch provides the important function of serving as a detent or coacting means for interlocking with the clutch actuating means or fork to prevent relative rotation of the bearing carrier and the stationary race member suspended thereon relative to the guide member.
Referring again to Figure 1, it will be noted that the actuating fork 30 includes a rearwardly extending cantilever spring member 62 which normally is provided in accordance with prior art constructions to provide a preloading of the actuating fork against the actuat;ng face 28 of the bearing assembly preventing rattling and noise as a result of vibration. In the present instance, the provision of the V-shaped notch interlocks with the depending portion of the cantilever spring 62 thereby preventing relative rotation of the bearing carrier and the guide member. During assembly of the clutch release :' ' ' bearing assembly, it is not necessary to angularly position thc V-shaped notch to eEfect an interlocking with the cantilever spring since during the first clutch actuation, the torque applied to the bearing assembly will cause rotation of the bearing carrier until the V-shaped notch is aligned with the spring 62 whereafter the clutch release bearing assembly will be retained in fixed position on the guide member. It will be furtller noted in the arIangement ;Is illustrated in ~i~ure 1 that the axial thrust of the actuating fork 30 is trallsmitted directly to the bearing assembly 14 and not through the bearing carrier 6.
~ eferring now to Figure 2 of the drawings, an alternative embodiment of the clutch release bearing assembly is illustrated in which like parts are designated by the same numeral as employed in Figure 1 with a prime affixed thereto.
As shown, the assembly includes a tubular bearing carrier 6' on which a bearing assembly 14' is suspended and which includes a rotatable race member 16' for~ed with an outwardly projecting radial flange 18' defining an engaging face 20' adapted to eoact with the elutch release means of a rotary elutch assembly.
A plurality of anti-friction elements such as balls 22' are interposed between the rotatabie race member and a stationary race member 24' which is formed at its rearward end or ri~ht hand end as viewed in ~i$ure 2, with a radial annular face 28' disposed against a stabili~ation eollar or washer 64. An actuating fork 30' is disposed in bearing contact against the opposite face of the stabilization eollar 64 and includes a cantilaver spring 62' adayted to be disposed in interlocking relationship within the V-shaped groove formed in the radial flan~e 5~' of the bearing earrier.
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As in the e~se of tl-e eml)odiment illustrated in Pigure 1, the arr~n~ement Or ligure 2 includes a spring washer 32' interlocked around the bearin~ carrier 6' by means of a groove 34' and is disposed with its peripheral portion in pre-loaded axial biased contact against the axial surfaces of an annular groove 36' which extends inwardly of a eireular bore 38' through the stationary race member 24'. The arrangement illustrltod in iig~lre 2 ;s similar to th3t previolJs~y deseribed in eonneetion with ~igure 1 and provides for similar self-alignment adjustment with respect to eccentrie misali~nment co~ditions and angular misalignment conditions of the axis of the guide member relative to the axis of rotation of the rotary clutch and release means thereon. The principal distinction resides in the relative disposition of the rotary and stationary raee members providing for a heavy duty cluteh release bearing assembly providing for increased life under heavy loads at high rotational speeds. The provision of the stabilization collar 64 is optional and is preferably eomprised of a blank steel washer whieh is disposed in the form of a press fit around the periphery of the bearing earrier 6'. The stabilization eollar 64 provides for added baeking support to the stationary race member 24' and further supports the clineh-butt joint of the bearing carrier in aceordance with the arrangement illustrated in Figure 3.
Referring now to Pigures S and 6 of the drawings, still another ~lternative embodiment of a elutch release bearing assembly is illustrated in which the outer race member is stationary while the inner race member is rotatable and wherein tho stationary race member is supported by a wave spring engaged J i ~
. ' ~ . ' ' in the periphery thereof in contrast to the embodiment illus-trated in Figure 2 in which the wave spring is engaged in a groove in the inner surface of the stationary race member. As shown in ~igures 5 and 6, the clutch release bearing assembly comprises a composite bearing carrier consisting of a tubular member 66, an oval-shaped flange 68 affixed to the rearward or right hand portion of the tubular member as viewed in Figure 5 alld all a~ ]ly projectillg ;~nntllar hollsing 70 encircling a bearing assembly 72. The inner surfilce of the tubular member 66 is formed with a groove 74 and a plurality of indentations 76 fo~ retaining a lubricant such as grease, facilitating reciproeat-ing movement of the lubular member along a guide tube (not shown) such as the tube 8 illustrated in phantom in Figure 1. The oval-shaped flange 68 is seeurely mounted on the tubular member 66 by means of a press fit within a groove on the right hand end of the tubular member as viewed in Figure 5. The tubular member is provided with a radial annular flange 77 to further seeure the assembly together. The ends of the flange 68 are bent to form a pair of rearwardly,extending tabs or ears 78 provided with apertures 80 for securing the bearing carrier to an aetuating fork (not shown).
The annular housing 70 extends in spaeed substantially eoncentric relationship with respect to the periphery of the tubular member 66 and is seeured to the flange 68 by means of bent tabs 82 disposed in interloeking engagement in recesses 84 formed along the edge of the flange as best seen in Figure 6.
The flange 68 is conveniently produeed by a stamping operation and is formed to provide two arcuate recesses 86 which project axially forwardly of the plane of the flange and are adapted to , .:
abut the inner edge of a station.lry race mcml>er 88 of the bearing Dssembly 72 maintaining it in al)propriate axinlly spaced relationship. The periphery or outer surf:~ce of the stationary race mem~er is disposed in radial clearance re-lationship with respect to the inner surface of the annular housing to provide for restricted radial shifting movement of the benring assembly relative to the composite bearing carrier.
For this purpose, the exterior surface of the stationary race member SS is formed with an inwardly extending annular groove 90 in which the inner edge portion of a wave spring 92 is seatably engaged in a manner similar to that previously described in connection with Figures 1 and 2. The inner edge of the wave spring 92 is disposed in clearance relationship with respect to the base of the annular groove 90 to permit restricted radial shifting movement of the bearing assembly relative to the composite bearing carrier to provide for correction of an eccentric misalignment condition. Similarly, the wave spring is def~ectable to also permit angular tilting of the bearing assembly to correct for an angular misalignment condition in a manner as previously described.
The outer edge of the wave spring 92 is disposed in engaging and supported relationship against the inner annulaT
surface of the housing 70. The outer or left hand end of the housing 70 as viewed in Figure S is formed with an inwardly directed flange 9~ to prevent inadvertent extraction of the bearing assembly from the housing.
The bearing assembly 72 may be of any of the types previously described and includes a rotatable inner race member 96 of a length projecting axially beyond the end of the .~ , .:
6!:) tubular mcmbcr 66 forming an nnnul.lr contact face 98 which is adaptcd to cngarc the clutch rclease fingcrs in a manncr as previously dcscribcd. Thc intcrnal surfacc o~ the inner race membcr 96 is spaccd in radial clcarance rclationship with respect IO the periphery of the tubular member to permit radial shifting movements as well as angular tilting movements of the bearing assembly to correct for misalignment conditions.
As shown in Figurc 5 a plllr~lity of anti-friction elcmellts or balls 100 arc interposed bctwcell the stationary and rotatable spaced relationship by means of a cage 102. An elastic annular seal 104 is secured along the forward inner edge of the stationary race member 88 and extends radially inwardly in sealing engagement with the peripilery of the rotatable race member. The seal 104 serves to retain a suitable lubricant such as grease ~ithin the bearing assembly. An annular disc 106 overlies the inner or right hand end of the bearing races as viewed in Figure S to restrict entry of con-taminating substances into the bearing assembly.
It will be apparent from the arrangement of the bearing assembly illustrated in Figures 5 and 6 that radial and angular shifting movements of the bearing assembly are permitted in a manner as previously described in connection with Figures 1 and 2. The axial thrust load from the actuating fork connected to the ears 78 of the composite bearing carrier is transmitted through the arcuate recesses 86 of the flange directly to the inner end of the stationary race member.
As prcviously described in connection with the embodi-ment shown in Figure 1 the inner diameter of the spring washcr 32 in a free unstressed condition is slightly smallcr than the ' ' ' `
diameter of the base of tlle groove 34 o~ t11e bearing earrierwhereby the spring washer i5 in a cireumferentially binsed eondition when seated in tl~e groove with the inner edges thcreof in gripping engagement around the be~ring carrier restricting relative movement therebetween. Similarly, in conneetion with the embodiment shown in Figures 5 and 6, the outer diameter of the spring washer in a free, unstressed condition is slightly larger t}lan tlle internal di~meter of the an?lular housing such that the syrinS w;lsiler is in a circulnferentially biased con-dition when positioned within the housing in accordance with the arrangement shown in Figure 5 such that the outer edges thereof are disposed in gripping engagement with the housing restricting relative rotative movement therebetween.
In order to further increase the gripping engagement between the spring washer 32 and the groove 34 of the bearing earrier 6, 6' in accordance with the arrangement shown in Figures 1 and 2, the ends of a wave spring 108 as shown in Figure 7 can be provided with inwardly directed barbs or burrs 110 which are adapted to bite or become embedded in the soft metal surface of the bearing carrier within the grooves 34, 34' thereby forming a mechanical interloek therebetween. The base of the groove 34, 34' can also be provided with surface roughness or irregularities in addition to the butt joint eonnection 45, as best seen in Figure 3 to further increase the frictional and mechanical gripping or interlock between the wave spring and the bearing carrier preventing relative circumferential movement therebetween. When the wave spring 108 of Figure 7 is employe~l in the arrangement illustrated in Figure 5, the barbs 110 project radially outwardly from the periphery of the spring _19_ .r so as to become embedded and mechallieally interloeked with the surface of tlle annular hol-sing 70. The form~tion of the baros 110 on the ends of the wave spring c~n be conveniently formed during the shearing of the wave spring strip into individual lengths prior to coilin~.
It is also eontemplated that in lieu of the barbs 110 of the embodiment illustrated in Figure 7, a wave spring 112 as shown in Figure S can be formed such that the terminnl portions thereof are of a reduced radius so th;lt the shnrp inwardly direeted eorners or edges 114 thereof ~end to beeome embedded and mechanically interlocked in the softer base metal of the grooves 34, 34' of the bearing carrier. Alternatively, a wave spring 116 is illustrated in Figure 9 in which the terminal portions of the spring are of an increased radius such that the sharp terminal edges 118 thereof project outwardly and are adapted to become embedded in the inner surface of the annular housing 70 of the embodiment illustrated in Figure 5.
Still another alternative embodiment of a wave spring 120 is illustrated in Figure 10 in which the inner and/or outer edges thereof are provided with staked V-shaped notches to provide a plurality of inwardly directed barbs 122 as well as outwardly directed barbs 124 disposed at circumferentially spaced intervals around the wave spring thereby further enhancing a mechanical gripping interaction with the base of the groove of the bearing carrier in accordance with the embodiments of Figure 1 and 2 or with the inner surface of the annular housing in accordance with the embodiment of Figure 5, respectively.
`. ', ~Q9t~46 While it will be ~pparent th.lt the invention herei disclosed is well calculated to acllieve tlle benefits and advant~ges as hcreinabove set forth, it will be ~ppreciate~
th~t the invention is susceptiblc to modification, variation and chan~e without departing from the spirit thereof.
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Claims (18)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A clutch release bearing assembly including a tubular bearing carrier, a bearing supported on said bearing carrier including a stationary race member, a rotatable race member, and a plurality of anti-friction elements interposed between said race members, said bearing assembly being mounted with an internal surface disposed in radial spaced clearance relationship relative to the outer periphery of said bearing carrier and said stationary race member including an annular, radially extending groove having a pair of side walls and an end wall, the improvement comprising: an annular spring washer with one edge portion in axially biased preloaded engagement with. the side walls of said groove but spaced-apart from said end wall to permit restricted radial shifting movement between said carrier and said bearing and restricted angular displacement of the axis of said bearing relative to the axis of said carrier, said spring washer including plural layers of a helically wound serpentine strip of resilient material and engaging means on said carrier for retaining said spring washer in longitudinally fixed position therealong.
2. The assembly set forth in Claim 1 wherein said spring washer includes antirotation means for preventing rotation between said spring washer and said bearing carrier.
3. The assembly as set forth in Claim 2 wherein said antirotation means includes at least one barb resiliently biased toward engagement with said bearing carrier,
4. The assembly as set forth in Claim 3 wherein said barb is disposed on the end of said spring washer.
5. The assembly as set forth in Claim 2 wherein said antirotation means includes a plurality of barbs disposed at circumferentially spaced intervals along the edge portion of said spring washer facing said bearing carrier.
6. The assembly as set forth in Claim 2 wherein said antirotation means includes an edge corner of an end of said spring washer being radially offset from the normal position to bias said edge corner into engagement with said bearing carrier.
7. The assembly as set forth in Claim 1 wherein said engaging means on said bearing carrier comprises an external groove around the periphery thereof for interlockingly receiving the inner-edge portion of said spring washer.
8. The assembly as set forth in Claim 1 wherein said tubular bearing carrier includes a radially extending flange formed with a radially extending notch therein defining said coacting means for interlocking engagement with the clutch actuating means preventing relative rotation of said carrier.
9. The improvement as defined in Claim 8 in which said radially extending flange is integrally formed on said carrier.
10. The improvement as defined in Claim 9 wherein said notch is of a generally outwardly directed V-shaped configuration for interlockingly receiving the clutch actuating means.
11. A clutch release bearing assembly including a tubular bearing carrier, a bearing supported on said bearing carrier including a stationary race member, a rotatable race member, and a plurality of anti-friction elements interposed between said race members, said stationary race member formed with an internal surface disposed in radial spaced clearance relationship relative to the periphery of said bearing carrier, an annular groove extending inwardly of said internal surface, a spring washer disposed with its outer edge portion in axially biased preloaded engagement within said groove and its inner edge portion in supporting relationship with said bearing carrier to permit restricted radial shifting movement between said carrier and said bearing and restricted angular displacement of the axis of said bearing relative to the axis of said carrier, said spring washer comprising plural layers of a helically wound serpentine strip of spring steel.
12. In an automobile power train or the like including a rotatable clutch having clutch release assembly, a guide mem-ber disposed substantially coaxial with the axis of rotation of the clutch and clutch actuating means the clutch release assembly being slidably mounted on the guide member and reciprocable therealong by the clutch actuating means for con-tacting the clutch release assembly said clutch release assembly comprising a hearing carrier including a tubular member slidably mounted on the guide member, a bearing supported in radial spaced clearance relationship on said bearing carrier including a plurality of anti-friction elements interposed between a stationary race member and a rotatable race member, said rotatable race member formed with an engaging face for engaging the clutch release means, the improvement comprising: said station-ary race member including an annular, radially extending groove, an annular spring washer disposed with one edge portion thereof in supported relationship on said bearing carrier and with the other edge portion thereof in axially biased preloaded engagement within said groove to permit restricted radial shifting movement between said bearing carrier and said bearing and restricted angular displacement of the axis of said bearing relative to the axis of said carrier, said spring washer including plural layers of a helically wound serpentine strip of resilient material.
13. The improvement as defined in Claim 12 in which said groove is formed by a pair of spaced substantially parallel radially extending walls terminating in a circular inner wall spaced in clearance relationship from said other edge portion of said spring washer.
14. The improvement set forth in Claim 12 in which said spring washer includes antirotation means for preventing rotation between said spring washer and said bearing carrier.
15. The improvement set forth in Claim 14 wherein said antirotation means comprises at least one barb resiliently biased toward engagement with the surface of said bearing carrier.
16. The improvement set forth in Claim 15 wherein said barb is disposed on the end of said spring washer.
17. The improvement set forth in Claim 14 wherein said antirotation means includes a plurality of barbs disposed at circumferentially spaced intervals along the edge portion facing said bearing carrier.
18. The improvement set forth in Claim 14 wherein said antirotation means includes an edge corner of an end of said spring washer being radially offset from the normal position to bias said edge corner into engagement with said bearing carrier.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US89047378A | 1978-03-27 | 1978-03-27 | |
| US890,473 | 1978-03-27 | ||
| US06/009,247 US4276974A (en) | 1978-03-27 | 1979-02-05 | Self-aligning clutch release bearing |
| US9,247 | 1979-02-05 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1098460A true CA1098460A (en) | 1981-03-31 |
Family
ID=26679249
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA324,117A Expired CA1098460A (en) | 1978-03-27 | 1979-03-26 | Self-aligning clutch release bearing |
Country Status (14)
| Country | Link |
|---|---|
| US (1) | US4276974A (en) |
| AR (1) | AR216223A1 (en) |
| AU (1) | AU4540679A (en) |
| BR (1) | BR7901816A (en) |
| CA (1) | CA1098460A (en) |
| DE (1) | DE2912036A1 (en) |
| ES (1) | ES478975A1 (en) |
| FR (1) | FR2421304A1 (en) |
| GB (1) | GB2019523A (en) |
| IN (1) | IN150532B (en) |
| IT (1) | IT1111554B (en) |
| MX (1) | MX148928A (en) |
| NL (1) | NL7902368A (en) |
| SE (1) | SE7902735L (en) |
Families Citing this family (27)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE7910203U1 (en) * | 1979-04-07 | 1979-07-05 | Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt | CLUTCH RELEASE |
| DE3008403A1 (en) * | 1980-03-05 | 1981-09-10 | Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt | RELEASER FOR CLUTCHES, ESPECIALLY FOR MOTOR VEHICLE CLUTCHES |
| FR2505954A1 (en) * | 1981-05-15 | 1982-11-19 | Valeo | CLUTCH FASTENING, IN PARTICULAR FOR A MOTOR VEHICLE, METHOD FOR FITTING SUCH A CLUTCH FASTENING ON A CONTROL FORK, AND CONTROL ROTTEN SUITABLE FOR SUCH A METHOD |
| DE3119367C1 (en) * | 1981-05-15 | 1982-12-09 | Bayerische Motoren Werke AG, 8000 München | Device for the hydraulic actuation of a drawn friction clutch for motor vehicles |
| FR2507354B1 (en) * | 1981-06-09 | 1986-03-28 | Valeo | CONTROL FORK FOR RELEASE CLUTCH, MOUNTING METHOD THEREOF, CLUTCH DEVICE COMPRISING SAME, AND RELATED CLUTCH STOP |
| US4534458A (en) * | 1982-01-25 | 1985-08-13 | Federal-Mogul Corporation | Self-aligning clutch release bearing assembly |
| FR2521237B1 (en) * | 1982-02-05 | 1987-03-20 | Valeo | RELEASE STOP, ESPECIALLY FOR A MOTOR VEHICLE |
| US4601374A (en) * | 1982-04-22 | 1986-07-22 | Federal-Mogul Corporation | Hydraulic clutch piston and seal |
| FR2538060B1 (en) * | 1982-12-15 | 1988-07-08 | Valeo | RELEASE STOP MOUNTING, PARTICULARLY FOR MOTOR VEHICLE |
| US4739867A (en) * | 1986-06-30 | 1988-04-26 | Aetna Bearing Company | Self-aligning bearing |
| US4883154A (en) * | 1988-06-02 | 1989-11-28 | Federal-Mogul Corporation | Self-aligning bearing carrier |
| JPH0610226Y2 (en) * | 1988-12-05 | 1994-03-16 | 三興線材工業株式会社 | Clutch device |
| FR2662769B1 (en) * | 1990-06-05 | 1992-08-14 | Valeo | DEVICE FOR CONTROLLING A CLUTCH, PARTICULARLY FOR MOTOR VEHICLES, FORMING A UNIT ASSEMBLY. |
| US5150778A (en) * | 1991-05-31 | 1992-09-29 | Federal-Mogul Corporation | Self-aligning clutch release bearing assembly |
| DE4304964C2 (en) * | 1992-02-28 | 2001-11-22 | Valeo | Clutch release bearings, in particular for motor vehicles |
| DE9321503U1 (en) | 1992-02-28 | 1998-10-01 | Valeo, Paris | Clutch release bearings, in particular for motor vehicles |
| FR2714944B1 (en) * | 1994-01-07 | 1996-03-01 | Valeo | Improved self-centering clutch release bearing. |
| FR2747441B1 (en) * | 1996-03-25 | 1999-12-10 | Valeo | ASSEMBLY OF THE RELEASE STOP |
| US6177770B1 (en) * | 1999-09-14 | 2001-01-23 | Pharmacopeia, Inc. | Article comprising an incremental positioner |
| US6637942B2 (en) | 2001-10-03 | 2003-10-28 | Dresser-Rand Company | Bearing assembly and method |
| US7066653B2 (en) | 2001-10-03 | 2006-06-27 | Dresser-Rand Company | Bearing assembly and method |
| US8316523B2 (en) * | 2009-10-01 | 2012-11-27 | Pratt & Whitney Canada Corp. | Method for centering engine structures |
| DE102011007660A1 (en) * | 2011-04-19 | 2012-10-25 | Hilti Aktiengesellschaft | Hand tool and manufacturing process |
| DE102013220248A1 (en) * | 2012-11-07 | 2014-05-08 | Schaeffler Technologies Gmbh & Co. Kg | Hydraulic cylinder, in particular for a clutch actuator in a motor vehicle |
| AU2014203984B2 (en) | 2013-01-03 | 2017-06-01 | Graco Minnesota Inc. | High pressure inlet swivel for hose reel |
| US9261147B1 (en) | 2014-06-10 | 2016-02-16 | Perfection Hy Test Company | Installation error proof clutch release bearing and method of installation in clutch fork |
| EP3242834B1 (en) | 2015-01-07 | 2018-11-28 | LORD Corporation | Aircraft engine mount |
Family Cites Families (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1606127A (en) * | 1923-04-03 | 1926-11-09 | Bullard Machine Tool Company | Bearing for clutch-releasing devices and other purposes |
| US2995406A (en) * | 1957-07-08 | 1961-08-08 | Roulements A Aiguilles Sa | Clutch thrust bearing and device equipped with the latter |
| GB1007475A (en) * | 1964-06-19 | 1965-10-13 | Ford Motor Co | Linearly movable clutch fork |
| FR1467848A (en) * | 1965-12-20 | 1967-02-03 | Ferodo Sa | Release bearing, and clutch comprising it |
| US3877557A (en) * | 1970-06-26 | 1975-04-15 | Luk Lamellen & Kupplungsbau | Clutch bearing having radial and axial free play |
| GB1310331A (en) * | 1971-02-04 | 1973-03-21 | Ford Motor Co | Self-centering clutch release bearing assembly |
| DE2156161B2 (en) * | 1971-11-12 | 1980-12-04 | Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl | Clutch release mechanism with self-centering release bearing |
| DE2221231C3 (en) * | 1972-04-29 | 1981-12-10 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Self-centering clutch release bearing |
| DE2230992C3 (en) * | 1972-06-24 | 1983-11-24 | Fichtel & Sachs Ag, 8720 Schweinfurt | Centrally guided roller bearing release for friction clutches |
| JPS5824652B2 (en) * | 1972-10-18 | 1983-05-23 | エス カ−ル エフ インダストリアル トレイデイング アンド デベロツプメント カンパニイ ビ−ヴイ | Shinawasekuratsuchijikuuke |
| JPS505751A (en) * | 1972-12-09 | 1975-01-21 | ||
| IT1011574B (en) * | 1973-05-15 | 1977-02-10 | Roulements Soc Nouvelle | THRUST HOLDER FOR CLUTCH CLUTCHES |
| US3931875A (en) * | 1973-12-26 | 1976-01-13 | Federal-Mogul Corporation | Self-aligning clutch bearing assembly |
| DE2457352A1 (en) * | 1974-12-04 | 1976-06-10 | Schaeffler Ohg Industriewerk | Bearing for clutch release mechanism - which is mounted with radial play on a guide shaft |
| DE2507194A1 (en) * | 1975-02-20 | 1976-09-02 | Skf Kugellagerfabriken Gmbh | SELF-CENTERING CLUTCH THRUST BEARING |
| FR2304829A1 (en) * | 1975-03-21 | 1976-10-15 | Ferodo Sa | RELEASE STOP |
| US4142618A (en) * | 1975-07-08 | 1979-03-06 | Skf Compagnie D'applications Mechaniques | Resilient self-aligning clutch release bearing |
| US4143748A (en) * | 1975-07-26 | 1979-03-13 | Luk Lamellen Und Kupplungsbau Gmbh | Disengaging bearing for clutches of motor vehicles |
| FR2320460A1 (en) * | 1975-08-05 | 1977-03-04 | Skf Cie Applic Mecanique | SELF-CENTERING CLUTCH STOPPER |
| DE7608859U1 (en) * | 1976-03-23 | 1976-08-19 | Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt | CLUTCH RELEASE WITH A SELF-CENTERING CLUTCH THRUST BEARING |
| SE414661B (en) * | 1976-03-31 | 1980-08-11 | Skf Kugellagerfabriken Gmbh | Compression sleeve |
| US4117917A (en) * | 1976-08-04 | 1978-10-03 | Federal-Mogul Corporation | Clutch throw-out bearing improvement |
-
1979
- 1979-02-05 US US06/009,247 patent/US4276974A/en not_active Expired - Lifetime
- 1979-03-26 IT IT21295/79A patent/IT1111554B/en active
- 1979-03-26 CA CA324,117A patent/CA1098460A/en not_active Expired
- 1979-03-26 GB GB7910532A patent/GB2019523A/en not_active Withdrawn
- 1979-03-26 MX MX177053A patent/MX148928A/en unknown
- 1979-03-26 IN IN200/DEL/79A patent/IN150532B/en unknown
- 1979-03-26 FR FR7907570A patent/FR2421304A1/en not_active Withdrawn
- 1979-03-26 AU AU45406/79A patent/AU4540679A/en not_active Abandoned
- 1979-03-26 BR BR7901816A patent/BR7901816A/en unknown
- 1979-03-27 DE DE19792912036 patent/DE2912036A1/en not_active Withdrawn
- 1979-03-27 AR AR275957A patent/AR216223A1/en active
- 1979-03-27 ES ES478975A patent/ES478975A1/en not_active Expired
- 1979-03-27 SE SE7902735A patent/SE7902735L/en unknown
- 1979-03-27 NL NL7902368A patent/NL7902368A/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| IT7921295A0 (en) | 1979-03-26 |
| GB2019523A (en) | 1979-10-31 |
| AR216223A1 (en) | 1979-11-30 |
| MX148928A (en) | 1983-07-12 |
| AU4540679A (en) | 1979-10-04 |
| IN150532B (en) | 1982-11-06 |
| BR7901816A (en) | 1979-11-20 |
| SE7902735L (en) | 1979-09-28 |
| US4276974A (en) | 1981-07-07 |
| FR2421304A1 (en) | 1979-10-26 |
| NL7902368A (en) | 1979-10-01 |
| ES478975A1 (en) | 1979-11-16 |
| DE2912036A1 (en) | 1979-10-11 |
| IT1111554B (en) | 1986-01-13 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |